Classifications

• • H—ELECTRICITY
  • H01—ELECTRIC ELEMENTS
  • H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
  • H01L21/00—Processes or apparatus adapted for the manufacture or treatment of semiconductor or solid state devices or of parts thereof
  • H01L21/02—Manufacture or treatment of semiconductor devices or of parts thereof
• • H—ELECTRICITY
  • H01—ELECTRIC ELEMENTS
  • H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
  • H01L21/00—Processes or apparatus adapted for the manufacture or treatment of semiconductor or solid state devices or of parts thereof
  • H01L21/67—Apparatus specially adapted for handling semiconductor or electric solid state devices during manufacture or treatment thereof; Apparatus specially adapted for handling wafers during manufacture or treatment of semiconductor or electric solid state devices or components ; Apparatus not specifically provided for elsewhere
  • H01L21/67005—Apparatus not specifically provided for elsewhere
  • H01L21/67011—Apparatus for manufacture or treatment
  • H01L21/67098—Apparatus for thermal treatment
  • H01L21/67109—Apparatus for thermal treatment mainly by convection
• • H—ELECTRICITY
  • H01—ELECTRIC ELEMENTS
  • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
  • H01J37/00—Discharge tubes with provision for introducing objects or material to be exposed to the discharge, e.g. for the purpose of examination or processing thereof
  • H01J37/32—Gas-filled discharge tubes
  • H01J37/32009—Arrangements for generation of plasma specially adapted for examination or treatment of objects, e.g. plasma sources
  • H01J37/32082—Radio frequency generated discharge
• • H—ELECTRICITY
  • H01—ELECTRIC ELEMENTS
  • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
  • H01J37/00—Discharge tubes with provision for introducing objects or material to be exposed to the discharge, e.g. for the purpose of examination or processing thereof
  • H01J37/32—Gas-filled discharge tubes
  • H01J37/32431—Constructional details of the reactor
  • H01J37/32458—Vessel
  • H01J37/32522—Temperature

Definitions

• serial number 60/059,173 entitled “Device and Method for Detecting and Preventing Arcing in RF Plasma Systems”
• serial number 60/059,151 entitled “System and Method for Monitoring
• serial number 60/065,794 entitled “All-Surface Biasable and/or Temperature-Controlled Electrostatically-Shielded RF Plasma Source.”
• the present application is also related to co-pending application serial number 60/095,035 (attorney docket number 2312-0720-6 YA PROV), entitled "ESRF COOLANT DEGASSING
• the present invention is directed to a method and system for cooling a plasma processing system, and in particular to a method and system for utilizing: (1) coolants that are expanded through an orifice and converted to gas that is applied to an exterior of a process tube and (2) an electrostatic shield that cools the processing tube by evaporating coolant using evaporation orifices in the electrostatic shield and directing the cooled vapor onto the process
• RIE reactive ion etching
• PECVD plasma enhanced chemical vapor deposition
• PVD ion assisted vapor deposition
• U.S. patent number 5,234,529 to Wayne L. Johnson, the inventor of the present application.
• RF radio frequency
• RF power is inductively coupled to the plasma using a helical coil.
• the four main sources of adsorbed gas are: (1) gas already trapped in the liquid prior to shipment (i.e., gas that was adsorbed prior to receipt by the plasma processing system user), (2) gas adsorbed into the liquid when the liquid is exposed to air, e.g., during pouring between containers before using the liquid, (3) gas adsorbed when air in the chamber is replaced by fluid during an initial filling cycle, and (4) the presence of air in any part of the system when fluid is being pumped.
• gas may be adsorbed into the coolant after the coolant pumps are stopped. When the pumps stop, if coolant in the high parts of the system drains to lower parts, then air replaces the drained coolant. When the pumps are restarted, the air may be broken down into bubbles which become another source of adsorbable gas.
• a method and system utilizing coolant that is evaporated as it passes through a shield (prior to being applied to the exterior of a process tube) to remove the heat generated in an RF powered plasma source.
• the present invention removes heat by vaporizing the liquid coolant and then pumping away the vapor. This method avoids the arcing that occurs in systems using baths of liquid coolant.
• the dielectric constant of the material around the coil remains close to the same between air and the dielectric fluid, the ESRF cavity can be tuned in air and will remain tuned over a wide range of temperatures. (That is, it is possible to reduce the shift in tuning that would otherwise result from a temperature-based change in the dielectric constant.)
• a method and system utilizing a process tube that is cooled using a shield which surrounds the process tube.
• a series of expansion orifices e.g., disposed along the ribs of the shield
• the coolant is vaporized as it exits the orifices. That vapor is then impinged upon the process tube to remove heat from the shield and the process tube. Heat is removed through one or more of (1) forced convection of cool vapor over the surface of the process tube and (2) conduction.
• Figure 1 is a schematic illustration of fluid flow according to the present invention
• Figure 2 is an illustration of a multiple spray nozzle cooling shield
• Figure 3 A is an expanded view of the interface between the manifold and a rib of the shield of Figure 2;
• Figure 3B is an expanded view of openings (either orifices or gas holes) in the multiple spray nozzle cooling shield shown in Figure 2;
• Figure 4 is an illustration of a multiple orifice cooling rib shield
• Figure 5 is an expanded view of orifices in the multiple orifice cooling rib shield shown in Figure 4;
• Figure 6 is an expanded view of orifices in the multiple orifice cooling rib shield shown in Figure 4 which apply the cooled vapor to a bias shield;
• Figures 7A and 7B are a chart showing the cooling characteristics of various commercially available coolants.
• ESRF systems are cooled without encountering problems previously associated with the use of untreated liquid coolants, namely arcing around helical coils.
• One embodiment of the invention uses a liquid dielectric that is evaporated and applied to hot surfaces, rather than submerging the hot surfaces in a liquid coolant.
• FIG. 1 is a schematic illustration of a cooled ESRF processing system that utilizes vaporized coolant as a replacement for baths of liquid coolants.
• an ESRF plasma source 100 is cooled by a source cooling chamber 105 using a vapor to remove heat from heated surfaces.
• a coolant is pumped from a fluid mass storage chamber 110 by a high pressure pump 115 through a length of tubing 117 and subsequently through a valve 120a.
• the pressure of the coolant is measured by a high pressure manometer 125a.
• the coolant then passes through a remotely controllable valve 130, through which the coolant mass flow rate is controlled.
• the coolant Upon exiting the mass flow controller 130, the coolant enters a manifold 305 (atop the shield 300; see Figure 2) that distributes coolant to the ribs 303 of the shield. As described, the coolant enters the ribs at a pressure (1) greater than the pressure maintained within the source cooling chamber 105 and (2) less than the coolant vapor pressure.
• the pressure difference between the coolant entering the ribs of the shield and the vapor environment of the source cooling chamber 105 is such that, as the coolant emerges from an expansion orifice, it expands, hence, reducing the pressure to below its vapor pressure. At this point the coolant changes phase from a liquid to a gas.
• the gas As the gas continues to expand to the ambient pressure within the source cooling chamber 105, it cools further (converting thermal energy to kinetic energy). Therefore, heat is transported away from the process tube by two mechanisms, namely: (1) conductive-convective heat transfer between the coolant (liquid state) and the process tube, and (ii) conductive-convective heat transfer between the process tube and the cool vapor impinging upon its surface.
• the shield ribs are, in turn, cooled by the first two mechanisms. Heat is transported to the coolant (in liquid state) as it flows through the manifold and ribs of the shield prior to passage through the expansion orifices 135.
• the heat transfer rate is proportional to (1) the surface area of the coolant conduits (within the distribution manifold and the shield ribs), (2) the temperature difference between the process tube (that is loosely thermally coupled to the ribs) and the shield ribs, and (3) the heat transfer coefficient.
• the heat transfer coefficient is primarily dependent upon the coolant flow rate and the coolant thermal properties (i.e., thermal conductivity, viscosity, specific heat at constant pressure, density, etc.).
• heat is expelled from the shield ribs as the latent heat for vaporization of the coolant (necessary for the coolant to change phase from a liquid state to a gas state) is provided by both the hot shield ribs and contact of the coolant with the process tube.
• the heat transfer rate is proportional to the latent heat of vaporization and the coolant mass flow rate.
• the third mechanism represents direct heat transfer between the process tube and the cool vapor as it impinges upon the process tube surface.
• the heat transfer rate is proportional to the process tube surface area, the temperature difference between the process tube and the impinging gas, and the heat transfer coefficient.
• the heat transfer coefficient is dependent upon the total area of expansion orifices, the distance between the orifice and the process tube, the gas velocity, and several gas properties (including the thermal conductivity, viscosity, specific heat at constant pressure, density, etc.).
• the previously cooled gas absorbs heat in the source cooling chamber 105 and is eventually pumped through another length of pipe and a valve 120b before entering a condenser 140.
• the vapor goes through a reverse phase change, being converted back to a liquid.
• heat is removed from the vapor as it becomes a liquid.
• the liquid then is pumped again by the high pressure pump 115.
• the process of pressurizing the liquid in pump 115 typically adds thermal energy to the liquid, the liquid is first passed through a heat exchanger 145 in which heat can be given off before returning the liquid to the fluid mass storage chamber 110 for another cycle.
• the high pressure manometer 125a and a second manometer 125b measure pressures at two locations in the cooling cycle — one before expansion and one after expansion. From the two pressures, a flowrate of the liquid and vapor can be determined. Using the flowrate, the cooling cycle can be controlled by controlling the flow control valve 130 to maintain a flow rate which provides a sufficient amount of vaporized coolant without creating a pool of coolant within the source cooling chamber 105.
• the system also includes a vacuum pump 160 connected on the vapor side of the expansion orifice 135. This pump is used to evacuate the system of air before operation begins.
• the amount of vacuum created by the vacuum pump 160 is (1) controlled by valves 120c and 120d and (2) measured by the vacuum pressure manometer 155.
• the vacuum pump 160 can likewise be controlled to pump more or less based on the reading of the manometer 155. After evacuating the system, the system is checked for leaks and then back-filled with a predetermined charge of coolant.
• the fluid mass storage chamber 110 also includes a residual contaminant relief valve.
• This valve can be used to bleed off gaseous contaminants that rise to the top of the fluid mass storage chamber.
• the relief valve is either pressure activated or manually controlled.
• the above method is preferably used in conjunction with either the multiple spray nozzle cooling shield 300 shown in Figure 2 (see close-up in Figure 3B) or with the multiple orifice cooling rib shield 360 shown in Figure 4. Both of these shields are advantageous since they provide fluid to be vaporized in sufficient quantities to remove the local heat load but without generating micro-bubbles on the surface of the coils.
• the shields are electrostatic shields rather than just cooling shields. The rate at which the vapor is pumped out of the chamber must be higher than that for a liquid coolant since the vaporized coolant displaces a larger volume than the corresponding liquid before the phase change. (However, the flow rate of the present invention is less than the flow rate of conventional systems.
• the present invention allows a 100 joule pickup for an equivalent flow.
• the system controls flow of the liquid coolant to ensure that the liquid coolant is substantially completely vaporized prior to being applied to the process to be (or the bias shield as described in further detail below).
• substantially complete vaporization allows the vapor to be applied without causing arcing in liquid coolant.
• multiple ribs 303 of the shield 300 are arranged to provide uniform cooling of the outside of a process tube 400 that is housed a short distance (0.125- 0.375 inch) inside of the shield 300.
• coolant is pumped into the shield 300 through the manifold 305 (via coolant entry hole 320 shown in Figure 2) and forced through drill holes 308 (located at the bottom of the manifold 305 and at the top of rib 303).
• drill holes 308 located at the bottom of the manifold 305 and at the top of rib 303.
• the coolant is then expelled through the openings 310.
• the openings 310 act as expansion orifices 135 and direct coolant towards an interior of the shield, i.e., towards an outer shell of the process tube 400.
• the drill hole 308 acts as the expansion orifice 135 for the corresponding rib 303.
• the openings 310 are simply holes large enough to allow the vaporized coolant to pass there through in a quantity sufficient to cool the process tube 400.
• the coolant entry hole 320 (shown in Figure 2) acts as a single orifice for the entire cooling system. Accordingly, the manifold 305 is filled with vaporized coolant. To accommodate the flow of vaporized coolant, the drill holes 308 and the openings 310 are enlarged as compared to when they carried liquid and/or acted as orifices 135.
• a multiple orifice cooling rib shield 360 contains multiple individual ribs 330, each with multiple orifices 340.
• Each orifice 340 is designed to cool a single rib 330 and a corresponding portion of the shield 360 adjacent to the rib.
• the shield 360 may either be a simple cooling shield or an electrostatic shield.
• the embodiment provides an additional heat transport mechanism compared to the first embodiment — i.e., conduction heat transfer between the process tube and the shield ribs as the shield ribs are cooled by the coolant latent heat of vaporization.
• orifices 340 increases as the area at the bottom of the conical shield 360 increases. This arrangement matches the need for more heat removal at the bottom of the shield 360.
• An enlarged section of a rib 330 is shown in Figure 5 with three orifices 340.
• the orifices are shaped and positioned so as to impinge streams of gas semi-perpendicular to the ribs such that the streams collide and disperse toward the wall of the process tube 400.
• the orifices are shaped and positioned so as to impinge streams of vapor directly onto the wall of the process tube 400.
• the streams are directed so as to cool their corresponding half of the portion of the process tube between adjacent ribs.
• the orifices 340 can be replaced by larger openings when the coolant has already been vaporized prior to or upon entering the rib 330 through the drill holes 308.
• the shield 360 is made of a thermally very conductive material in order to remove heat more evenly.
• the ribs 330 are further designed to have narrow cross sections opposing each other to minimize the capacitive coupling between adjacent ribs. Capacitive coupling across the gap in an electrostatic shield increases insertion loss of the electrostatic shield.
• Figure 6 shows another embodiment in which a slotted bias shield 410 is interposed between the process tube 400 and an electrostatic shield 360.
• the bias shield 410 receives heat from the process tube 400 and is cooled by the vapor rather than cooling the process tube directly.
• an electrical insulator is placed there between.
• the insulator depicted in Figure 6 is simply an air gap, other electrical insulators are possible.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Plasma & Fusion (AREA)
• Analytical Chemistry (AREA)
• Chemical & Material Sciences (AREA)
• General Physics & Mathematics (AREA)
• Microelectronics & Electronic Packaging (AREA)
• Power Engineering (AREA)
• Computer Hardware Design (AREA)
• Manufacturing & Machinery (AREA)
• Condensed Matter Physics & Semiconductors (AREA)
• Drying Of Semiconductors (AREA)
• Physical Or Chemical Processes And Apparatus (AREA)
• Chemical Vapour Deposition (AREA)

Priority Applications (5)

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Citations (3)

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• 1999
  • 1999-08-03 KR KR1020017001430A patent/KR100634654B1/ko not_active IP Right Cessation
  • 1999-08-03 EP EP99937746A patent/EP1102869A4/en not_active Withdrawn
  • 1999-08-03 US US09/774,183 patent/US6385977B1/en not_active Expired - Fee Related
  • 1999-08-03 JP JP2000563849A patent/JP2002522212A/ja not_active Withdrawn
  • 1999-08-03 WO PCT/US1999/017516 patent/WO2000008229A1/en active IP Right Grant
  • 1999-08-03 CN CN998103519A patent/CN1131892C/zh not_active Expired - Fee Related
• 2002
  • 2002-03-26 HK HK02102280.3A patent/HK1042529B/zh not_active IP Right Cessation

Patent Citations (3)

Non-Patent Citations (1)

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